Structure for control valve

ABSTRACT

A structure for a control valve fluidly disposed between a fluid source and a fluid-pressure operated actuator, comprises a valve housing defining therein an axial bore, a stationary valve member press-fitted into the axial bore and having a portion projected out of the axial bore, a solenoid plunger slidably disposed on an outer periphery of the projected portion of the stationary valve member, a fluid flow regulating valve portion formed on the outer periphery of the projected portion of the stationary valve member and the inner periphery of the plunger, for regulating a flow of working fluid passing therethrough to the actuator, a return spring for biasing the plunger in one axial direction; and an electromagnetic solenoid disposed on an outer periphery of the plunger, for axially sliding the plunger against the bias of the biasing means in response to a control signal.

This is a divisional of copending U.S. application Ser. No. 08/155,176,filed on Nov. 19, 1993.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a valve structure for a control valvesuitably applied to a fluid pressure control valve which variablycontrols the outgoing fluid pressure and to a fluid flow control valvewhich variably controls a rate of the output fluid flow therethrough,and specifically to an electromagnetic solenoid-type fluid pressurecontrol valve which is applied to a hydraulic brake system with ananti-skid brake control system generally abbreviated as an "ABS" and/ora traction control system generally abbreviated as a "TCS", and furtherto an electromagnetic solenoid type fluid flow control valve which isapplied to a steering effort control system for an automotive vehicle inwhich the steering effort can be suitably controlled depending on thevehicle speed.

2. Description of the Prior Art

Recently, there have been proposed and developed various electromagneticsolenoid type fluid pressure control valves which can properly vary theincoming fluid pressure to generate a controlled fluid pressure to afluid-pressure operated actuator, such as a vehicle wheel cylinder. Forexample, Japanese Utility Model First Publication (Jikkai Heisei) No.3-68685 discloses an electromagnetic solenoid type fluid pressurecontrol valve which includes a valve housing with an axial bore and asubstantially cylindrical valve spool slidably enclosed in the axialbore. Such a pressure control valve is usually arranged between anexternal fluid pressure source and a fluid-pressure operated actuatorsuch as a wheel brake cylinder, so as to suitably control the outgoingfluid pressure therethrough to the actuator. The valve spool itself isintegrally formed with a pair of solenoid plunger portions at both endsof the central valve portion of the valve spool. The respective solenoidplungers are arranged axially to the central valve portion in such amanner as to extend in the opposing axial directions of the valve spool.Therefore, the axial length of the valve spool would become large.

Japanese Patent First Publication (Tokkai Shows) No. 3-65461 discloses abrake control system for automotive vehicles, which is applied commonlyto an anti-skid brake control and a traction control. The brake controlsystem includes a master-cylinder equipped with a hydraulic brake forcebooster, four three-port/three-position, electromagnetic solenoid-typeswitching valves which are included in the ABS and arranged parallel toeach other between the master cylinder and the respective wheelcylinders, and two two-port/two-position electromagnetic solenoid-typeswitching valves which are included in the TCS and arranged in the brakefluid line between the master cylinder and the driven-wheel cylinders.As appreciated from the above, the brake control system disclosed in theJapanese document No. 3-65461 requires a number of electromagneticsolenoid-type switching valves for an anti-skid brake control executedduring deceleration slip and a traction control executed duringacceleration slip. The above-mentioned plural switching valves are notintegrally formed as a single unit, but constructed independently ofeach other. Thus, the prior art system suffers from the drawback thatthe entire size and whole weight of the system tend to be both enlargedto provide many advantageous functions, namely a deceleration-slipcontrol, an acceleration-slip control, the functioning of a hydraulicbrake booster, or the like. It is troublesome to install the brakecontrol system in a relatively narrow limited space of the vehicle.

SUMMARY OF THE INVENTION

It is, therefore in view of the above disadvantages an object of thepresent invention to provide a small-sized and lightweight control valvestructure in which the axial length of the valve can be limited at aminimum.

It is another object of the invention to provide an improved fluidpressure control valve unit which contributes commonly to an anti-skidbrake control system and a traction control system, and is compact toreduce the entire weight and size of the system and to enhance themounting efficiency of the system.

It is a further object of the invention to provide an improved fluidflow control valve unit which contributes to a steering effort controlsystem for an automotive vehicle and enables the construction of thesystem to be simplified and the assembly of the system on the vehicle tobe facilitated.

In brief, the above objects are achieved by a coaxial arrangement of anelectromagnetic solenoid-type control valve constructed as a singlevalve unit, i.e., by a coaxial arrangement between at least oneelectromagnetic solenoid, a solenoid plunger serving as a slidable valvespool and a stationary valve member which is stationarily disposed in avalve casing and axially extends along the central axis of the valve.Additionally, the improved fluid pressure control valve includes anaxially slidable pilot piston which engages the solenoid plunger at oneend thereof and receives a master-cylinder pressure at the other endthereof for moving the plunger in a pressure buildup direction by thereceived master-cylinder pressure, and an axially slidable reactionpiston which receives a controlled fluid pressure at one end thereof andengages the plunger at the other end and is disposed in an axial bore ofthe stationary valve member for moving the plunger in a pressurereduction direction.

According to one aspect of the invention, a structure for a controlvalve fluidly disposed between a fluid source and a fluid-pressureoperated actuator, comprises a valve housing defining therein an axialbore, a stationary valve member press-fitted into the axial bore andhaving a portion projected out of the axial bore, a solenoid plungerslidably disposed on an outer periphery of the projected portion of thestationary valve member, a fluid flow regulating valve portion formed onthe outer periphery of the projected portion of the stationary valvemember and the inner periphery of the plunger, for regulating a flow ofworking fluid passing therethrough to the actuator, means for biasingthe plunger in one axial direction, and an electromagnetic solenoiddisposed on an outer periphery of the plunger, for axially sliding theplunger against the bias of the biasing means in response to a controlsignal.

According to another aspect of the invention, a structure for a controlvalve fluidly disposed between a fluid source and a fluid-pressureoperated actuator, comprises a valve housing defining therein an axialbore, a cylindrical stationary valve member press-fitted into the axialbore and having a portion projected out of the axial bore, a cylindricalsolenoid plunger slidably coaxially arranged with the stationary valvemember so that an inner peripheral surface of the plunger slidablyengages an outer peripheral surface of the projected portion of thestationary valve member, the plunger being cooperative with thestationary valve member to define at least one variable throttlingorifice on the two opposing peripheral surfaces, for regulating a flowrate of working fluid flowing through the orifice to the actuator byvarying a throttling rate of the orifice depending on an axial positionof the plunger to the stationary valve member, a return spring forbiasing the plunger in one axial direction, and an electromagneticsolenoid coaxially arranged on an outer periphery of the plunger, foraxially sliding the plunger against the bias of the spring in the otheraxial direction by an axial displacement based on a value of excitingcurrent applied to the solenoid.

According to a further aspect of the invention, a structure for a fluidpressure control valve fluidly disposed between an external fluidpressure source and a fluid-pressure operated actuator and between afluid reservoir and the actuator, comprises a valve housing definingtherein an axial bore, a cylindrical stationary valve memberpress-fitted into the axial bore and having a portion projected out ofthe axial bore, a cylindrical solenoid plunger slidably coaxiallyarranged with the stationary valve member so that an inner peripheralsurface of the plunger slidably engages an outer peripheral surface ofthe projected portion of the stationary valve member, the plunger beingcooperative with the stationary valve member to define first and secondvariable throttling orifices on the two opposing peripheral surfaces,the first orifice fluidly disposed between the external fluid pressuresource and the actuator for providing a restricted high-pressure fluidflow to the actuator, and the second orifice fluidly disposed betweenthe reservoir and the actuator for providing a restricted low-pressurefluid flow to the actuator, by varying throttling rates of the first andsecond orifices such that a throttling rate of one orifice is increasedwhen a throttling rate of the other orifice is decreased depending on anaxial position of the plunger to the stationary valve member, a returnspring for biasing the plunger in one axial direction, and anelectromagnetic solenoid coaxially arranged on an outer periphery of theplunger, for axially sliding the plunger against the bias of the springin the other axial direction by an axial displacement based on a valueof exciting current applied to the solenoid.

According to a still further aspect of the invention, a structure for afluid flow control valve fluidly disposed between an external fluidpressure source and a fluid-pressure operated actuator, comprises avalve housing defining therein an axial bore, a cylindrical stationaryvalve member press-fitted into the axial bore and having a portionprojected out of the axial bore, a cylindrical solenoid plunger slidablycoaxially arranged with the stationary valve member so that an innerperipheral surface of the plunger slidably engages an outer peripheralsurface of the projected portion of the stationary valve member, theplunger being cooperative with the stationary valve member to define onevariable throttling orifice on the two opposing peripheral surfaces, forregulating a flow rate of working fluid flowing therethrough to theactuator, by varying a throttling rate of the orifice depending on anaxial position of the plunger to the stationary valve member, a returnspring for biasing the plunger in one axial direction, and anelectromagnetic solenoid coaxially arranged on an outer periphery of theplunger, for axially sliding the plunger against the bias of the springin the other axial direction by an axial displacement based on a valueof exciting current applied to the solenoid.

According to another aspect of the invention, a structure for a fluidpressure control valve fluidly disposed between a first fluid pressuresource and a fluid-pressure operated actuator and between a fluidreservoir and the actuator, comprises a valve housing defining thereinfirst and second axial bores separated from each other and axiallyaligned with each other, a cylindrical stationary valve memberpress-fitted into the first axial bore and having a portion projectedout of the first axial bore, a cylindrical solenoid plunger slidablycoaxially arranged with the stationary valve member so that an innerperipheral surface of the plunger slidably engages an outer peripheralsurface of the projected portion of the stationary valve member, theplunger being cooperative with the stationary valve member to define atleast one variable throttling orifice on the two opposing peripheralsurfaces, for regulating a fluid pressure of working fluid fed from thefirst fluid pressure source to the pressure control valve, by varying athrottling rate of the orifice depending on an axial position of theplunger to the stationary valve member, a return spring for biasing theplunger in a pressure, reduction direction in which the regulated fluidpressure from the pressure control valve to the actuator is reduced, areaction piston slidably axially disposed in the projected end of thestationary valve member and receiving the regulated fluid pressure at aninnermost end thereof, for and pushing the plunger by an outermost endthereof and for returning the plunger in the pressure reductiondirection, and electromagnetic solenoid means coaxially arranged on anouter periphery of the plunger, for axially sliding the plunger inproportion to a value of attraction force based on a value of excitingcurrent applied to the solenoid means. The control valve structure mayfurther comprise a pilot piston slidably accommodated in the secondaxial bore and receiving a pilot pressure fed from a second fluidpressure source at one end thereof, for pushing the plunger by the otherend thereof in a pressure buildup direction in which the regulated fluidpressure is increased. It is preferable that a pressure-receiving areaof the pilot piston may be designed to be greater than that of thereaction piston by a predetermined amplification. Alternatively, thecylindrical stationary valve member may be formed with a steppedprojected portion, and the plunger may include an annular groove beingtrapezoidal in cross-section in such a manner as to fit the outerperipheral surface of the stepped valve member, thereby causing theplunger to move in the pressure reduction direction by reaction createdby the difference between the pressure-receiving areas of the axiallyopposing annular side walls defining the singular groove.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is an enlarged longitudinal cross-sectional view illustrating afirst embodiment of a fluid pressure control valve according to theinvention.

FIG. 2 is a schematic system diagram illustrating a brake fluid pressurecontrol system incorporating the fluid pressure control valve of thefirst embodiment.

FIG. 3 is a graph illustrating fluid pressure characteristics of thefluid pressure control valve of the first embodiment.

FIGS. 4A and 4B is a timing chart illustrating two waveforms of dithercurrents applied to a solenoid activated in a phase of an anti-skidbrake control and a solenoid activated in a phase of a traction control,respectively.

FIG. 5 is a graph illustrating a fluid pressure characteristic of thefluid pressure control valve of the first embodiment during applicationof the dither current.

FIG. 6 is an enlarged longitudinal cross-sectional view illustrating asecond embodiment of the fluid pressure control valve in which thesolenoid is de-activated.

FIG. 7 is an enlarged cross-sectional view illustrating the pressurecontrol valve of the second embodiment in the solenoid-activated state.

FIG. 8 is an enlarged longitudinal cross-sectional view illustrating athird embodiment of the pressure control valve in thesolenoid-deactivated state.

FIG. 9 is an enlarged cross-sectional view illustrating the pressurecontrol valve of the third embodiment in the solenoid-activated state.

FIG. 10 is an enlarged longitudinal cross-sectional view illustrating afourth embodiment of the pressure control valve, wherein upper and lowerhalves respectively showing one valve condition in thesolenoid-activated state and the other valve condition in thesolenoid-deactivated state.

FIG. 11 is an enlarged longitudinal cross-sectional view illustrating afifth embodiment of the pressure control valve, wherein upper and lowerhalves respectively showing one valve condition in thesolenoid-activated state and the other valve condition in thesolenoid-deactivated state.

FIG. 12 is an enlarged longitudinal cross-sectional view illustrating asixth embodiment of the pressure control valve, wherein upper and lowerhalves respectively showing one valve condition in thesolenoid-activated state and the other valve condition in thesolenoid-deactivated state.

FIG. 13 is an enlarged longitudinal cross-sectional view illustrating aseventh embodiment of the pressure control valve, wherein upper andlower halves respectively showing one valve condition in thesolenoid-activated state and the other valve condition in thesolenoid-deactivated state.

FIG. 14 is an enlarged longitudinal cross-sectional view illustrating aneighth embodiment of the pressure control valve, wherein upper and lowerhalves respectively showing one valve condition in thesolenoid-activated state and the other valve condition in thesolenoid-deactivated state.

FIG. 15 is a graph illustrating fluid-flow throttling amount and strokeversus exciting-current characteristics in the pressure control valve ofthe eighth embodiment.

FIG. 16 is an enlarged longitudinal cross-sectional view illustrating aninth embodiment of the pressure control valve in thesolenoid-deactivated state.

FIG. 17 is an enlarged cross-sectional view illustrating the pressurecontrol valve of the ninth embodiment in the solenoid-activated state.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

In a plurality of embodiments, the fluid pressure control valves recitedin the first to seventh embodiments respectively incorporating astructure of a control valve according to the invention are exemplifiedin case of a brake fluid pressure control valve applied to a brakecontrol system incorporated in an automotive brake system, while thefluid flow control valve recited in the eighth and ninth embodimentsrespectively incorporating a structure of a control valve according tothe invention are exemplified in case of a steering effort controlsystem such as an automobile power steering.

First embodiment

Referring now to FIGS. 1 through 5, particularly to FIG. 2, the brakefluid pressure control system incorporating the fluid pressure controlvalve of the first embodiment includes a tandem master cylinder 2connected to a main brake line for producing a master-cylinder pressuredepending on the depressing amount of a brake pedal 2a, four wheel brakecylinders 3 respectively attached to rear-left, rear-right, front-leftand front-right road wheels, an external brake-fluid pressure source 6,a brake fluid reservoir T, and a brake controller 13. For the purpose ofsimplification of the disclosure, only one fluid pressure control valve7a is fluidly disposed in the brake line arranged between the mastercylinder 2 and the associated wheel brake cylinder 3. The external fluidpressure source 6 includes a fluid pressure pump 6a, a pair of checkvalves 6b fluidly disposed just upstream and downstream of the pump 6a,a pressure accumulator 6c temporarily storing a high-pressure brakefluid pressurized by the pump 6a, a pressure switch 6d responsive to achange in the brake-fluid pressure at the outlet port of the accumulator6c, and a relief valve 6e fluidly connected to the accumulator 6c forrelieving excessive pressure discharged from the pump, and an additionalcheck valve 6b disposed downstream of the pressure switch 6d forpreventing back-flow from the pressure control valve 7a back to thepressure switch.

Referring now to FIG. 1, the fluid pressure control valve 7a of thefirst embodiment includes a pair of electromagnetic solenoids 5a and 5bcontributing respectively to a traction control and to an anti-skidbrake control. The solenoid 5a includes a solenoid body B₁ and anexciting coil portion K₁, while the solenoid 5b includes a solenoid bodyB₂ and an exciting coil portion K₂. The respective solenoids 5a and 5balso include a common coil casing 52 and an axially slidable commonsolenoid plunger 4. The solenoid plunger 4 which is cylindrical inshape, also serves as a pressure controlling valve spool. The solenoidbodies B₁ and B₂ consist of a substantially cylindrical common base 51,a pair of intermediate cylindrical members 56a and 56b respectivelyattached to both ends of the base 51 in a manner so as to bepress-fitted onto the outer periphery thereof, and a pair of attractingmembers 58a and 58b respectively press-fitted into the ends of theintermediate cylindrical members 56a and 56b. The coil portion K₁ iscomprised of an exciting coil 53a, a bobbin 55a made of non-magneticmaterial and winding thereon the coil 53a, and the protective coilcasing 52, while the coil portion K₂ is comprised of an exciting coil53b, a bobbin 55b made of non-magnetic material and winding thereon thecoil 53b, and the coil casing 52. As seen in the left-hand side of FIG.1, the attracting member 58a includes a flanged portion 58f forreceiving the left end of the coil portion K₁. Reference numeral 60denotes an intermediate partition arranged for separating the twosolenoids 5a and 5b. The boss-like portion of the left-hand sideattracting member 58a, the intermediate cylindrical member 56a, the base51, the intermediate cylindrical member 56b, and the right-hand sideattracting member 58b are cooperative to each other to form acylindrical solenoid support. When assembling the solenoids, the coilportion K₁, the intermediate partition (50, the coil portion K₂ areinserted and mounted on the solenoid support in that order, andthereafter the coil casing 52 is abutted with the shoulder portion ofthe right-hand side attracting member 58b to hermetically cover theouter peripheries of the coil portions and K₂ and the partition 60. Asseen in the rightmost end of FIG. 1, the attracting member 58b has amale-screw portion. The coil casing 52 is firmly secured onto theshoulder of the attracting member 58b by means of a fastening nut 59screwed onto the male-screw portion of the latter, In this manner, thecoil portions K₁ and K₂ are detachably mounted on the cylindricalsolenoid support so that a damaged coil portion is easily exchangeablefor new parts. The thickness of the intermediate partition 60 isrestricted to a minimum value necessary to avoid electromagneticinterference between the two solenoid coils K₁ and K₂, with the resultthat the two coils K₁ and K₂ are axially arranged adjacent to eachother. The attracting members 58a and 58b, the coil casing 52, theintermediate partition 60, the base 51, and the plunger 4 arerespectively made of magnetic material, to provide a path for a magneticloop. The attracting member 58a is formed with a magnetic leakage edge61a having a triangle in cross-section, so as to cause the solenoid 5ato produce magnetic attracting force for the plunger 4. Similarly, theattracting member 58b is formed with a magnetic leakage edge 61b havinga triangle in cross-section, so as to cause the solenoid 5b to producemagnetic attraction for the plunger

As shown in FIG. 1, the base 51 has an axial bore 57 serving as aplunger chamber or a spool chamber in which the solenoid plunger 4(valve spool) is slidably accommodated. Thai is, the solenoid bodies B₁and B₂ both including common base 51 serve as the valve housing for thepressure control valve 7a. The left attracting member 58a has an axialbore into which a substantially left half of a cylindrical shaft-likestationary valve member 1 is press-fitted. The cylindrical plunger 4 hasan axial bore 4a through which the plunger 4 is slidably fitted on asubstantially right half of the stationary valve member 1. The plunger 4is made of magnetic material to cause axial sliding movement byattraction caused by the energized solenoid. A substantially cylindricalflanged stopper 42 is press-fitted into the right opening end of theplunger 4 to abut one end of a reaction piston as hereinbelow describedin detail. The stopper 42 has at least one communication fluidpassageway 42a.

The stationary valve member 1 has a hydraulic pressure supply port 11aand a drain port 11b, each of which consists of an annular groove formedon the outer periphery of the right-half projecting portion of the valvemember 1. The supply port 11a is connected to the fluid pressure source6 through an elongated axial bore 11d in the valve member 1, an annulargroove 11t formed on the outer periphery of the valve member 1, aninclined communication passageway 11w formed in the left attractingmember 58a and a line 14. The drain port 11b is connected to thereservoir tank T through an axially extending pressure relief groove 11fformed on the outer periphery of the valve member 1, the axial bore 4afacing the stopper 42, the communication passageway 42a, a portion ofthe plunger chamber 57 facing the right end of the plunger 4, anelongated axial bore 4c formed in the plunger 4, an inclinedcommunication passageway 11g formed in the left attracting member 58aand a line 16. The stationary shaft-like member 1 has a controlled fluidpressure port 11c which is connected to either one of the wheel brakecylinders 3 and arranged midway between the two annular ports 11a and11b. The controlled fluid pressure port 11c actually consists of aradially extending through opening. The port 11c is connected to thewheel cylinder 3 through an elongated axial communication passageway 11eformed parallel to the axial bore 11d in the valve member 1, aninlet-and-outlet port 11u formed in the left attracting member 58a and aline 17. Thus, atmospheric pressure is introduced into the port 11c. Thecylindrical plunger 4 is formed with an annular communication groove 4bin such a manner as to establish a fluid communication between the twoports 11a and 11c or between the to ports 11b and 11c. The communicationgroove 4b constantly communicates with the controlled fluid pressureport 11c. An intermediate land 11s is defined between the two annulargroove-like ports 11a and 11b, in a manner which blocks the respectivefluid communications between the ports 11a and 11c and between the ports11b and 11c, in a centralized neutral position of the plunger 4. Asappreciated from FIG. 1 wherein the solenoid plunger 4 is conditioned inits neutral position, the left end of the above-mentioned land 11s iscooperative with the annular communication groove 4b to define avariable throttling orifice s, while the right end of the land iscooperative with the communication groove 4b to define a variablethrottling orifice t. In other words, a main fluid pressure regulatingvalve potion is defined on the radially opposing peripheral surfaces ofthe valve member 1 and the plunger 4. When the plunger 4 slides on thestationary valve member 1 leftwards (viewing FIG. 1) from the neutralposition, the orifice s becomes opened and the orifice t is fully closedsuch that the opening degree of the orifice s is gradually increased inaccordance with an increase in the leftward sliding movement of theplunger 4. Thus, the wheel-cylinder pressure is gradually increased inaccordance with the leftward sliding movement of the plunger 4.Conversely, when the plunger 4 slides on the stationary valve member 1rightwards from the neutral position, the orifice s is fully closed andthe orifice t becomes opened such that the opening degree of the orificet is gradually increased in accordance with an increase in the rightwardsliding movement of the plunger 4. In this manner, the controlled fluidpressure created by the fluid pressure control valve 7a is continuouslyvaried depending on a relative displacement of the plunger 4 to itsneutral position, in a manner so as to be increased according to theleftward axial movement of the plunger and to be decreased according tothe rightward axial movement of the plunger. In any case, since fluidpressure acting on the inner periphery of the plunger 4 is passedthrough the annular grooves 11a, 4b, or 11b, the fluid pressure actsuniformly on the inner periphery of the plunger 4. Such annular groovearrangement assures a smooth axial sliding movement of the plunger 4without causing undesirable friction owing to radial force acting on theplunger 4. As appreciated from FIG. 1, it is advantageous to coaxiallyarrange all of the coil portions K₁ and K₂, the coil casing 52, theattracting members 58a and 58b, the common base 51, the solenoid plunger4, and the stationary valve member 1, in order to effectively reduce thewhole length of the pressure control valve unit 7a.

A return spring 4d is disposed between the left end of the plunger 4 andthe attracting member 58a in its pre-compressed state, with the resultthat the plunger 4 is normally biased rightwards by way of the bias ofthe spring 4d. The plunger 4 is thus held in its rightmost positionunder the de-energized condition of the two solenoids 5a and 5b, withthe result that the orifice s is fully opened and therefore atmosphericpressure is introduced through the annular groove 4b into the controlledfluid pressure port 11c. The valve member 1 also includes an axial bore63 at the projected end. The axial bore 63 is formed to be aligned withthe central axis of the valve member 1 and communicates with the portlie. A parallel-pin type reaction piston 64 is slidably accommodated inthe axial bore 63 in such a manner as to receive the controlled fluidpressure at the left end thereof and to push the stopper 42 fatted tothe plunger 4 at the other end thereof. A pilot piston 65 is slidablydisposed in a central bore defined in the attracting member 58b. A pilotchamber 66 is defined by the eight end surface of the pilot piston 65and the inner wall of the central bore of the attracting member 58b.With this arrangement of the reaction piston 64, reaction created byabutment between the left end of the stopper 42 and the right end of thereaction piston 64 acts on the plunger 4 to cause a rightward movementof the plunger 4. The pilot chamber 66 is communicated with the outletport of the master cylinder 2 through a fixed orifice 68, apilot-pressure inlet port 67 and a line 15. The fixed orifice serves toprevent the sliding movement of the pilot piston 65 from being dampenedand to ensure a smooth sliding movement of the piston 65 with a highresponsiveness to the pilot pressure. The inlet port 67 receives themaster-cylinder pressure as a pilot pressure. With the above arrangementof the pilot piston 65, a leftwardly pushing force transmitted throughthe pilot piston 65 acts on the plunger 4 through the right end of thestopper 42.

In order to prevent undesirable magnetic field to cause and to enhancemagnetizing efficiency of the solenoid, it is preferable that aplurality of parts disposed in the vicinity of the above magnetizedmembers such as the attracting members 58a and 58b, the coil casing 52,the base 51, and the plunger 4 are made of non-magnetic material. In theembodiment, the stationary valve member 1, the stopper 42, the reactionpiston 64 and the pilot piston 65 are made of non-magnetic material,such as alumite, stainless steel, or the like.

When the left-hand side solenoid 5a is activated, attracting forcecreated by the solenoid 5a acts to cause a leftward sliding movement ofthe plunger 4 in the pressure buildup direction wherein the controlledfluid pressure is increased. For this reason, the solenoid 5a isoperated during traction control. The left-hand side solenoid 5a isgenerally referred to as a "TCS solenoid". In contrast to the above,when the right-hand side solenoid 5b is activated, attracting forcecreated by the solenoid 5b acts to cause a rightward sliding movement ofthe plunger 4 the pressure reduction direction wherein the controlledfluid pressure is reduced. The solenoid 5b is operated during anti-skidcontrol so as to reduce the wheel cylinder pressure. Thus, the fightsolenoid is generally referred to as an "ABS solenoid".

As appreciated from FIGS. 4A and 4B, a dither current which oscillatesaccording to a predetermined duty-cycle, is constantly applied to theTCS solenoid 5a and the ABS solenoid 5b, and as a consequence thesolenoid plunger 4 slightly oscillates. This micro-vibration preventsundesirable hysteresis of the controlled fluid pressure owing to slidingresistance of the plunger 4 and enhances a responsiveness of thepressure control valve. Upon application of the dither current to thesolenoid, the fluid pressure characteristics of a wheel-cylinderpressure versus a master-cylinder pressure exhibits slight positive andnegative pressure fluctuations with respect to a usual fluid pressurecharacteristic shown by the broken line of FIG. 5. As seen in FIGS. 4Aand 4B, a dither current applied to the ABS solenoid is conditioned inreverse phase to a dither current applied to the TCS solenoid, in orderto suppress undesirable axial displacement of the plunger 4 owing to thedither currents applied to the solenoids 5a and 5b.

Returning to FIG. 2, the brake controller 13 in general includes a TCScontrol unit and an ABS control unit, so as to drivingly control the TCSsolenoid 5a and the ABS solenoid 5b on the basis of detected signalsgenerated by a vehicle speed sensor 18 and a wheel speed sensor 19.

The fluid pressure control valve 7a of the first embodiment operates asfollows.

When the brakes are released, i.e., the brake pedal 2a is not depressed,the master-cylinder pressure becomes zero. Under this condition, theplunger 4 of the pressure control valve 7a is held in its rightmostposition by the bias of the spring 4d. As a result, the controlled fluidpressure becomes zero, because of the fully opened orifice t. Thus, thewheel-cylinder pressure is held zero.

When the brakes are applied, i.e., the brake pedal 2a is depressed, themaster-cylinder pressure is increased in response to an increase indepression of the pedal. During usual braking, the solenoids 5a and 5bare both deactivated, since the ABS and the TCS are held in-operative.In addition, the pump 6a is not driven under the in-operative conditionof the TCS. In the pressure control valve 7a, the master-cylinderpressure is applied to the right end of pilot piston 65 through thepilot-pressure inlet port 67, the orifice 68 and the pilot chamber 66.As shown in FIG. 1, the pilot piston 65 is pushed to the left and thusthe stopper is pushed to the left by the pilot piston. As a result, theplunger 4 moves leftwards against the bias of spring 4d, and thus theorifice s becomes opened. Thus, the controlled fluid pressure in theport 11c is increased, with the result that a fluid pressure in thefluid-pressure operated actuator, i.e., the wheel cylinder pressurebecomes increased. On the other hand, the reaction piston 64 receivesthe controlled pressure in the port 11c at the left end thereof, withthe result that the reaction piston 64 moves rightwards. Owing to therightward sliding movement of the reaction piston 64, the right end ofthe reaction piston 64 abuts and pushes the stopper 42. Reaction forceof the piston 64 is transmitted through the stopper 42 to the plunger 4,with the result that the plunger 4 is pushed to the right and returnstowards the spring set position. As a consequence, the plunger 4 is heldin a position at which the leftward pushing force caused by the pilotpiston 65 is balanced to the sum of the rightward biasing force createdby the spring 4d and the reaction force of the reaction piston 64. Notethat a pressure-receiving area of the pilot piston 65 employed in thepressure control vane 7a of the first embodiment is designed to begreater than that of the reaction piston 64. Under the above balancedstate, since the product of the controlled fluid pressure in the port11c and the pressure-receiving area of the reaction piston 64 is inproportion to the product of the master-cylinder pressure and thepressure-receiving area of the pilot piston 65, the ratio of the area ofthe pilot piston 65 to the area of the reaction piston 64 is necessarilyequivalent to the ratio of the controlled fluid pressure in the port 11cto the incoming master-cylinder pressure. Accordingly, as compared withthe master-cylinder pressure, the controlled fluid pressure in the port11c becomes multiplied by a predetermined amplification such as "9". dueto the ratio of the pressure-receiving area of the pilot piston 65 tothe pressure-receiving area of the reaction piston (54. In such apressure control valve structure, the wheel-cylinder pressure can beincreased with a high pressure gradient in accordance with an increasein the master-cylinder pressure, as appreciated from a wheel-cylinderpressure versus master-cylinder pressure characteristic indicated byBOOSTER of FIG. 3. That is, the pressure control valve itself canfunction as a compact hydraulic brake force booster. As appreciated fromthe above, the pressure control valve 7a of the first embodiment caneasily produce high braking force.

Alternatively, when the ABS control unit employed in the to brakecontroller 13 determines skidding of the road wheel owing to excessivebraking force exceeding frictional force between the tire and the roadsurface during quick braking or during braking on a low frictional road,for example wet, snow or icy roads, the ABS is put into operation.During operation of the ABS, the ABS controls the magnitude of theexciting current applied to the ABS solenoid 5b, depending on the sliprate of each road wheel. The slip rate is usually derived by the ABScontrol unit on the basis of the detected vehicle speed and the detectedwheel speed. On the other hand, the TCS is held in-operative, the pump6a is not driven and as a result only the master-cylinder pressure isintroduced to the pressure control valve 7a. The ABS operates to permitnormal application of the brakes by alternately reducing andintensifying the wheel-cylinder pressure of the skidding road wheel,such that braking can be held just below the point at which a skid wouldstart to develop. Upon the ABS solenoid 5b is energized during operationof the ABS, the exciting coil 53b produces a magnetic loop incooperation with the attracting member 58b, the coil casing 52, theintermediate partition 60, the common base 51 and the plunger 4, withthe result that the triangular magnetic leakage edge 61b generatesattracting force to attract the plunger 4 towards the right side. As aconsequence, the plunger 4 is moved rightwards by way of activation ofthe ABS solenoid 5b. The valve spool becomes kept in a position whereinthe leftward pushing force caused by the pilot piston 65 is balanced tothe sum of the rightward biasing force of the spring 4d, the reaction ofthe reaction piston 64, and the attraction created by the ABS solenoid5b. In this manner, the plunger 4 is slightly returned to the right sideowing to the attraction of the solenoid 5b, and thus the controlledfluid pressure is decreased to reduce braking force applied to theskidding road wheel. This prevents a skid of the road wheel. The brakecontroller 13 properly increases and decreases the magnitude of theexciting current applied to the ABS solenoid 5b on the basis ofcomparison of the detected slip rate with a predetermined allowable sliprate. As shown in FIG. 3, a wheel-cylinder pressure versusmaster-cylinder pressure characteristic can be varied within acontrolled pressure range indicated by ABS.

When the vehicle experiences acceleration slip of the driven wheelsowing to excessive driving force above friction between the road surfaceand the driven wheels during quick depression of the accelerator pedal,such as quick starting, quick acceleration, or the like, the TCS comesinto operation so as to suppress excessive driving force exerted on thedriven wheels and to enhance a controllability of the vehicle. Duringoperation of the TCS, the TCS is responsive to the slip rate of eachdriven wheel to control the magnitude of the exciting current applied tothe TCS solenoid 5a employed in the pressure control valve 7a. On theother hand, since the pump 6a of the external fluid pressure source 6 isdriven in response to the instruction from the TCS, the pressurizedfluid is introduced into the fluid-pressure supply port 11a. Uponactivation of the TCS solenoid 5a, the exciting coil 53a is cooperativeto the attracting member 58a, the coil casing 52, the intermediatepartition 60, the common base 51 and the plunger 4, so as to produce adesired magnetic loop. The triangular magnetic leakage edge 61agenerates the attraction to attract the plunger 4 towards the left side.As a consequence, the plunger 4 is moved leftwards by way of activationof the TCS solenoid 5a. The plunger 4 becomes kept in a position whereinthe attraction created by the TCS solenoid 5a is balanced to the sum ofthe rightward biasing force of the spring 4d and the reaction of thereaction piston 64. In this manner, the valve spool 4 is slightlyreturned to the left side owing to the attraction of the TCS solenoid5a, and thus the pressurized fluid is fed through the port 11a to theport 11c. As a result, the controlled fluid pressure is increased tobuild up braking force applied to the slipping road wheel. This reducesan acceleration-slip of the road wheel, The brake controller 13 properlycontrols the magnitude of the exciting current applied to the TCSsolenoid 5a on the basis of comparison of the detected slip rate with apredetermined allowable slip rate. As shown in FIG. 3, a wheel-cylinderpressure versus master-cylinder pressure characteristic can be variedwithin a controlled pressure range indicated by TCS.

As will be appreciated from the above, in the pressure control valve 7aof the first embodiment, since the valve spool 4 itself is formed as acommon solenoid plunger applied commonly to both the TCS solenoid 5a andthe ABS solenoid 5b and additionally the two solenoids 5a and 5b areaxially arranged adjacent to each other, the axial length of the valveunit 7a is effectively shortened. Thus, the whole weight of the valveunit 7a is also reduced, thereby enhancing the mounting efficiency ofthe valve unit 7a on the vehicle. The pressure control valve of thefirst embodiment is Constructed as a single valve unit having ahydraulic brake force booster function as well as the ABS-valve functionand the TCS-valve function, such a valve structure ensures alight-weight brake fluid pressure control system. Furthermore, since thesolenoid plunger 4, the reaction piston 64, and the pilot piston 65 areaxially aligned with each other along the central axis of the solenoids5a and 5b, the pressure-sensing parts such as the solenoid plunger, thereaction piston and the pilot piston can be compactly arranged in thecylindrical hollow defined in the solenoids, while preventingundesirable magnetic field to cause and enhancing magnetizing efficiencyof the solenoids.

Second embodiment

Referring now to FIGS. 6 and 7, there is shown the second embodiment ofthe fluid pressure control valve applied to a brake fluid pressurecontrol system. The, basic pressure control valve structure of thesecond embodiment as shown in FIGS. 6 and 7 is similar to that of thefirst embodiment as shown in FIGS. 1 through 5. Therefore, the samereference numerals used in the first embodiment will be applied to thecorresponding elements used in the second embodiment of FIG. 6, for thepurpose of lo comparison between the first and second embodiments,Furthermore, the same reference numerals as the first and secondembodiments will be applied to the third through ninth embodimentshereinafter described in detail, for the purpose of simplification ofthe disclosure.

Referring now to FIGS. 6 and 7, the fluid pressure control valve 7b ofthe second embodiment is different from the fluid pressure control valveof the first embodiment in that only a TCS solenoid 3c is provided andparts corresponding to an ABS solenoid and a pilot piston are notprovided. Therefore, in the second embodiment, the attracting member 58aof the first embodiment is replaced with a base 51a. The base 51 and theattracting member 58b of the first embodiment are replaced by only onepart, namely an base 51b. The base 51b has a communication drain port11b at the outside end thereof. The drain port 11h is connected to thereservoir tank T. The drain port 11b is connected through the pressurerelief groove 11f and the communication passageway 42a, and the drainport 11b to the reservoir tank T. The controlled fluid pressure port 11cis connected through the axial communication passageway 11e to thefluid-pressure operated actuator A, such as a wheel brake cylinder. Thefluid pressure control valve 7b of the second embodiment operates asfollows.

Under the de-energized condition of the solenoid 5c, the plunger 4 ismaintained in the leftmost position by way of the bias; of the spring4d, as shown in FIG. 6. As a result, the orifice s is fully closed andthe orifice t is opened, and thus the fluid pressure in the actuator Ais released to the tank T. Consequently, the fluid pressure in theactuator A becomes reduced. In contrast to the above, upon the solenoid5c is energized, the plunger 4 moves rightwards against the bias of thespring 4d by way of attracting force of the solenoid 5c, with the resultthat the orifice t is fully closed and the orifice s becomes opened, asshown in FIG. 7. As a result, the pressurized fluid is fed from theexternal fluid pressure source 6 through the axial bore 11d, the supplyport 11a to the annular communication groove 4b and the controlled fluidpressure port 11c to the actuator A. As a consequence, the fluidpressure in the actuator A is increased. As appreciated from the above,in the fluid pressure control valve 7b of the second embodiment, sincethe stationary valve member 1 and the cylindrical valve spool 4 servingas the solenoid plunger are coaxially arranged with each other, theentire axial length of the valve 7b can be shortened. In addition to theabove, since the solenoid plunger 4 also serves as the valve spool, thenumber of parts is reduced. This ensures lightening of the valve unit.

Third embodiment

Referring now to FIGS. 8 and 9, there is shown a fluid pressure controlvalve 7c of the third embodiment. The structure of the pressure controlvalve 7c of the third embodiment is basically similar to that of thesecond embodiment. The valve structure of the third embodiment isdifferent from that of the second embodiment in that the triangularmagnetic leakage edge 61a is formed at the base 51b but not at the base51a. Thus, in contrast to the pressure control valve 7b of the secondembodiment, when the solenoid 5d employed in the pressure control valve7c of the third embodiment is conditioned in its de-energized state, theplunger 4 is maintained in its rightmost position by the bias of thespring 4d, with the result that the orifice s is opened and thereforethe fluid pressure in the actuator A becomes increased. On the otherhand, when the solenoid 5d is energized, the plunger 4 is movedleftwards against the spring biasing force by way of attraction of thesolenoid 5d. As a result, the orifice t becomes opened and thus thefluid pressure in the actuator A is released to the reservoir T. As setforth above, the pressure control valve 7c of the third embodiment hasthe same effect as the pressure control valve 7b of the secondembodiment.

Fourth embodiment

Referring now to FIG. 10, there is shown a fluid pressure control valve7d of the fourth embodiment. The upper half of the valve 7d illustratedabove the one-dotted center line of FIG. 10 shows a valve spool positionunder the energized condition of the solenoid 5c, while the lower halfof the valve 7d illustrated below the center line shows a spring setposition of the valve spool 4 under the de-energized condition of thesolenoid 5e. The pressure control valve of the fourth embodiment isdifferent from that of the third embodiment in that the structure of thestationary valve member 1 and the fluid passageways of respective parts1 and 4 are different from those of the third embodiment. In the fourthembodiment, the stationary valve member 1 is a stepped shaft consistingof a left-hand side large-diameter portion 10a and a right-hand sidesmall-diameter portion 10b. The left end of the large-diameter portion10a is press-fitted into the axial bore of the attracting base 51b. Theright end of the small-diameter portion 10b is fitted into the axialbore of the base 51a in a fluid-tight fashion by means of a seal ring 69such as an O ring disposed between the outer periphery of thesmall-diameter portion 10b and the inner peripheral wall of the axialbole of the base 51a. The large-diameter portion 10a includes a radiallyextending pressure supply port 11j adjacent to the stepped portion ofthe valve member 1 and an axial bore 11k, while the small-diameterportion 10b includes a radially extending controlled fluid pressure port11c adjacent to the stepped portion, an axially extending pressuresupply bore 11m, and an axially extending pressure relief groove 11nformed on the outer periphery thereof. The axial bore 11k extends alongthe central axis of the stationary valve member 1 to intercommunicatethe radial bore 11j and an external fluid pressure port lip formed inthe base 51b. The axial bore 11m extends along the central axis of thestationary valve member 1 to intercommunicate the controlled fluidpressure port 11c and the inlet-and-outlet port 11u leading to theactuator A. The base 51a is formed with an inclined communication drainport or passageway 11h. The axial groove 11n is connected through theinclined drain port 11b to the reservoir T. The plunger 4 has a steppedbore 4a in such a manner as to slide along the stepped outer peripheryof the stationary valve member 1. A substantially annular communicationgroove 4b being a trapezium in cross-section is formed at the steppedsection of the stepped bore 4a of the plunger 4, such that the groove 4bconstantly communicates with the controlled fluid pressure port 11c. Theannular groove 4b is cooperative to the supply port 11j to define avariable throttling orifice s and is cooperative to the pressure reliefgroove 11n to define a variable throttling orifice t. As seen in FIG.10, the communication groove 4b is defined by a circumferentiallyextending cylindrical bottom wall surface, a right-hand side radiallyextending annular wall surface, and a left-hand side radially extendingannular wall surface which has the width less than the right-hand sideannular surface and opposes axially to the right-hand side annularsurface. In the annular groove structure of the valve of the fourthembodiment, the plunger 4 (valve spool) tends to be moved to the fight(viewing in FIG. 10) by way of reaction created by the difference of thepressure receiving areas between the two opposing annular wall surfacesof the groove 4b. Actually, the width difference between the twoopposing annular walls corresponds to the difference between the outsidediameters of the two portions 10a and 10b. That is to say, the plunger 4with the trapezoidal annular groove 4b operates as if the plunger itselfserves as a reaction piston.

As shown in the lower half of FIG. 10, under the deenergized conditionof the solenoid 5e, the plunger 4 is biased to the rightmost position bythe bias of the spring 4d, with the result that the orifice s is fullyclosed and the orifice t is opened. Thus, the working fluid in theactuator A is exhausted to the reservoir T through the port flu, theaxial bore 11m, the port 11c, the annular groove 4b, the pressure reliefgroove 11n, and the inclined communication drain port 11b. The fluidpressure in the actuator A is reduced, in the in-operative state of thesolenoid 5e. Conversely, as seen in the upper half of FIG. 10 in whichthe solenoid 5e is energized, the plunger 4 is moved to the leftmostposition against the bias of the spring 4d by way of attraction of thesolenoid 5e. As a consequence, the orifice t is fully closed and theorifice s becomes opened and thus external fluid pressure generated bythe fluid pressure source 6 is transmitted to the actuator A through theline 14, the external fluid pressure port 11p, the axial bore 11k, thesupply port 11j, the annular communication groove 4b, the port 11c, theaxial bore 11m, and the inlet-and-outlet port 11u. Thus, the fluidpressure in the actuator A tends to be intensified. In this case, thetwo opposing pressure-receiving annular surfaces of the groove 4breceive the controlled fluid pressure fed to the actuator A, and thusreaction created by the difference between the two pressure-receivingareas is also increased in accordance with an increase in the controlledfluid pressure. According to the increase in the reaction, the plunger 4is again returned to the right. Finally, the plunger 4 becomes kept in aposition wherein the attraction of the solenoid 5e is balanced to thesum of the rightward biasing force of the spring 4d and the above-notedreaction, Accordingly, the plunger 4 is slightly returned to the rightside owing to the reaction created by the two opposingpressure-receiving surfaces of the groove 4b. In this manner, thecontrolled fluid pressure can be controlled to a pressure valueproportional to a value of the exciting current applied to the solenoid5e. As sot forth above, in the pressure control valve 7d of the fourthembodiment, since the stationary valve member 1 and the solenoid plunger4 are arranged coaxially to each other, the entire axial length can beshortened, Although the stationary valve member I defines therein thetwo parallel axial bores lid and 11e in the pressure control valves 7a,7b and 7c of the first, second, and third embodiments, the stationaryvalve member 1 of the fourth embodiment includes the two axial bores 11kand 11m axially aligned to each other and separated from each other.Therefore, the outside diameter of the valve member 1 of the fourthembodiment can be small-sized as compared with the first to thirdembodiments. In addition to the above, since the plunger 4 of the fourthembodiment also serves as a reaction piston without providing thestopper 42 and the reaction piston 64, the number of parts of the valveunit can be minimized. In view of the foregoing, the structure of thepressure control valve 7d of the fourth embodiment is superior to thoseof the first to third embodiments.

Fifth embodiment

Referring now to FIG. 11, the upper half of FIG. 11 shows the energizedcondition of the solenoid 5f employed in the pressure control valve 7eof the fifth embodiment, while the lower half of FIG. 11 shows thede-energized condition of the solenoid 5f. The structure of the pressurecontrol valve 7e of the fifth embodiment is basically similar to thepressure control valve 7d of the fourth embodiment. As compared with thestructure of the control valve 7d of the fourth embodiment, thestationary valve member 1 and the plunger 4 both arranged in the valve7e of the fifth embodiment are reversed in the opposite axial direction.For these reasons, the two junctions between the actuator A and thevalve 7e and between the external fluid pressure source 6 and the valve7e are replaced with each other. Under the energized condition of thesolenoid 5f, the fluid pressure in the actuator A is reduced. Under thede-energized condition, the fluid pressure in the actuator A isintensified. Accordingly, the valve 7e of the fifth embodiment has thesame effect as the valve 7d of the fourth embodiment.

Sixth embodiment

Referring now to FIG. 12, the upper half of FIG. 12 shows the energizedcondition of the solenoid 5g employed in the pressure control valve 7fof the sixth embodiment, while the lower half of FIG. 12 shows thede-energized condition of the solenoid 5g. The structure of the pressurecontrol valve 7f of the sixth embodiment is basically similar to thepressure control valve 7d of the fourth embodiment, but the fluidpassageway structure of the control valve 7f of the sixth embodiment isdifferent from that of the control valve 7d of the fourth embodiment. Ascompared with the passageway structure of the control valve 7d of thefourth embodiment, the pressure relief groove 11n of the valve 7d isreplaced with an inclined pressure supply passageway 4e whichintercommunicates the annular communication groove 4b and the plungerchamber 57. In the sixth embodiment, the inclined drain port 11h of thecontrol valve 7d is replaced with an axially extending drain bore of thecontrol valve 7f, while the axial pressure supply bore 11m of thecontrol valve 7d is replaced with an inclined pressure supply port orpassageway of the control valve 7f. In the above-noted passagewaystructure of the valve 7f of the sixth embodiment, the controlled fluidpressure port 11c is thus replaced with a drain port 11r. As appreciatedfrom the above, the pressure control valve of the sixth embodiment hasthe same effect as the valve 7d of the fourth embodiment.

Seventh embodiment

Referring now to FIG. 13, the upper half of FIG. 13 shows the energizedcondition of the solenoid 5h employed in the pressure control valve 7gof the seventh embodiment, while the lower half of FIG. 13 shows thede-energized condition of the solenoid 5h. The structure of the pressurecontrol valve 7g of the seventh embodiment is basically similar to thepressure control valve 7f of the sixth embodiment, and the solenoidplunger of the control valve 7g has the same structure as that of thecontrol valve The valve 7g of the seventh embodiment is different fromthe valve 7f of the sixth embodiment in that the stepped valve member 1is comprised of two split parallel-pin-like members, namely alarge-diameter valve portion 10a and a small-diameter valve portion 10b.The large-diameter portion 10a is press-fitted into the axial boredefined in the left-hand side base 51b, while the small-diameter portion10b is press-fitted into the axial bore defined in the right-hand sidebase 51a. There is no oil leakage between the outer peripheral surfacesof the pin-like members 10a and 10b and the inner walls of the axialbores defined in the two bases 51a mid 51b. Therefore, the control valve7g of the seventh embodiment does not require a seal ring 69 fitted tothe inner wall of the valve 7f of the sixth embodiment. Accordingly, thecontrol valve 7g of the seventh embodiment has the same effect as thevalve 7f of the sixth embodiment.

Eighth embodiment

Referring now to FIG. 14, the upper half of FIG. 14 shows the energizedcondition of the solenoid 5j employed in the pressure control valve 8aof the eighth embodiment, while the lower half of FIG. 14 shows thede-energized condition of the solenoid 5j. In the eighth embodiment, thecontrol valve structure according to the invention is applied as a fluidflow control valve 8a of a steering effort control system, In the eighthembodiment, a main fluid flow regulating valve portion is defined on theradially opposing peripheral surfaces of the valve member 1 and theplunger 4. The flow control valve 8a includes a valve housing 20 whichhas two ports radially opposing to each other, namely a screw-threadedinlet port 21 and a screw-threaded outlet port 22. An electromagneticsolenoid 5j is attached to one side wall of the valve housing 20. Thesolenoid 5j is substantially similar to the solenoid 5d of the pressurecontrol valve 7c of the third embodiment, except for the point describedhereinbelow. The base 51a of the solenoid 5 j is positioned with respectto the valve housing 20 by way of a positioning pin 23 such as aparallel pin and thereafter the solenoid base 51a is firmly secured ontothe side wall of the housing 20 by bolts 24. In this manner, an axialbore 25 formed along the central axis of the housing 20 is axiallyaligned with the cylindrical plunger chamber 57 defined in the base 51aalong the central axis thereof. One end of the stationary valve member 1is press-fitted into the axial bore 25 of the housing, the other end isprojected into the plunger chamber The solenoid plunger 4 is slidablyreceived on the outer periphery of the projected portion of thestationary valve member 1. At least one radially extendingthrough-opening-like oil supply port 26 is formed in the projectedportion of the valve member 1. The plunger 4 includes a radially boredoil supply port 27, for feeding working fluid to the radial supply port26 therethrough. The valve member 1 also includes an axially extendingpressure supply communication bore 28 which intercommunicates thescrew-threaded outlet port 22 and the radial supply port 26. The plunger4 includes an axially extending communication passageway 29intercommunicating the supply port 27 and the screw-threaded inlet port21. With these arrangements, the radial supply port 26 of the stationaryvalve member 1 is cooperative with the supply port 27 of the plunger 4,to define a variable throttling orifice u which restricts and regulatesa flow rate of working fluid flowing from the inlet port 21 to theoutlet port 22. The radial supply port 26 has a substantially U-shapedradially extending tapered groove 26a at the rightmost end of the innerperiphery, for allowing a throttling rate of the orifice u to graduallyvary in accordance with an increase in rightward axial displacement ofthe plunger 4 to the valve member 1, and for avoiding excessive changein the throttling rate owing to the rightward movement of the plunger 4.The right-hand side base 51b includes a screw-threaded axial bore 30into which a spring-bias adjusting screw 31 is screwed, for adjusting aspring set force of a return spring 4d. A fastening nut 32 is screwedonto the male-screw threaded portion of the adjusting screw 31 andwhereby the adjusting screw 31 is completely locked to the base 51b andsimultaneously the solenoid coil casing 52 is fixed on the base 51b. Thebase 51b also defines an axial bore at the left half. A stopper pin 33is press-fitted into the axial bore of the base 51b, so that the maximumrightward axial movement of the plunger 4 is restricted by abutmentbetween the left end of the stopper pin 33 and the right end of thestopper 42 press-fitted into the plunger 4. The flow control valve 8a ofthe eighth embodiment operates as follows.

Under the de-energized condition of the solenoid 5j, the plunger 4 isbiased to its leftmost position by the bias of the spring 4d, as seen inthe lower half of FIG. 14. The throttling rate of the orifice u is setto a minimum value, that is, the flow rate through the orifice u is setto a maximum value at the leftmost plunger position wherein the stopper42 abuts the right end of the valve member 1. Under the energizedcondition of the solenoid 5j as seen in the upper half of FIG. 14, theplunger 4 is moved rightwards by attraction of the solenoid 5j, with theresult that the throttling rate of the orifice u is set to a maximumvalue, i.e., the flow rate through the orifice u is set to a minimumvalue at the rightmost plunger position wherein the stopper 42 abuts thestopper pin 33. As appreciated from the above, the plunger 4 is finallyheld in a balanced position in which the attracting force created by thesolenoid 5j is balanced to the bias of the spring 4d. As shown in FIG.15, the flow control valve 8a exhibits a plunger stroke versus solenoidexciting current characteristic and a flow rate versus solenoid excitingcurrent characteristic. As appreciated from the characteristicsillustrated in FIG. 15, the flow rate of the control valve 8a is variedin inverse proportion to a value of exciting current applied to thesolenoid 5j. In the flow control valve 8a of the eighth embodiment,since the plunger 4 also serving as the spool valve and the stationaryvalve member 1 are coaxially arranged with each other, the entire axiallength of the valve 8a can be shortened and consequently the number ofparts constructing the valve unit is reduced. This ensures alight-weight fluid flow control valve unit.

Ninth embodiment

Referring now to FIGS. 16 and 17, there is shown a fluid flow controlvalve 8b of the ninth embodiment. FIG. 16 shows one valve state whereinthe solenoid 5k is de-energized, while FIG. 17 shows the other valvestate wherein the solenoid 5k is energized. The structure of the flowcontrol valve 8b of the ninth embodiment is basically similar to that ofthe flow control valve 8a of the eighth embodiment, except for somepoints as detailed later. In the control valve 8b of the ninthembodiment, in addition to the plunger chamber 57, the base 51a isformed with the axial bore 25 as well as the plunger chamber 57, forrigidly tilting thereinto one end of the valve member 1. The base 51a isfirmly secured and screwed into the female-screw threaded hole 20adefined in the valve housing 20. The radial oil supply port 26 of thevalve member 1 consists of a plurality of radially extending throughopenings each having a relatively small diameter. Additionally, theplural through openings 26 are arranged to be offset from each other inthe axial direction of the valve member 1, with the result that thethrottling rate of the orifice u can be moderately varied in accordancewith an axial displacement or stroke of the plunger 4. In addition tothe effect obtained by the flow control valve of the eighth embodiment,the flow control valve 8b of the ninth embodiment can avoid misalignmentbetween the axial bore 25 receiving the valve member 1 and the plungerchamber 57 slidably accommodating the solenoid plunger 4 serving as thevalve spool, because the two bores 25 and 57 are coaxially formed in theidentical member, namely the base 51a. In the previously-describedsecond to ninth embodiments, the bases 51a and/or 51b serves as thevalve housing of the control valve unit.

According to the structure of the control valve of each embodiment,since the shaft-like valve member 1 and the solenoid plunger 4 arecoaxially aligned with each other, and the solenoid plunger itselfserves as the valve spool, and the solenoid base serves as the valvehousing, the entire axial length of the control valve is shortened andin addition the number of parts constructing the valve unit is reducedto a minimum, whereby the valve unit itself can be small-sized, whileinsuring a flow control performance or a pressure control performance ofthe valve unit.

In the previously-noted embodiments, although the valve spool 4 itself(plunger) is made of magnetic material, only the outer peripheralportion of the spool 4 or either one of right and left halves of thespool may be made of magnetic material.

While the foregoing is a description of the preferred embodimentscarried out the invention, it will be understood that the invention isnot limited to the particular embodiments shown and described herein,but that various changes and modifications may be made without departingfrom the scope or spirit of this invention as defined by the followingclaims.

What is claimed is:
 1. A structure for a fluid pressure control valvefluidly disposed between an external fluid pressure source and afluid-pressure operated actuator and between a fluid reservoir and saidactuator, comprising:a valve housing defining therein an axial bore; acylindrical stationary valve member press-fitted into said axial boreand having a stepped portion projected out of said axial bore; acylindrical solenoid plunger slidably coaxially arranged with saidstationary valve member so that an inner peripheral surface of saidplunger slidably engages an outer peripheral surface of the projectedportion of said stationary valve member, said plunger including anannular groove being trapezoidal in cross-section on the innerperipheral surface thereof, said annular groove being cooperative withtwo radial bores formed at both sides of the stepped section of saidstationary valve member to define first and second variable throttlingorifices, said first orifice fluidly disposed between said externalfluid pressure source and said actuator for providing a restrictedhigh-pressure fluid flow to said actuator, and said second orificefluidly disposed between said reservoir and said actuator for providinga restricted low-pressure fluid flow to said actuator, by varyingthrottling rates of said first and second orifices such that athrottling rate of one of said two orifices is increased when athrottling rate of the other orifice is decreased depending on an axialposition of said plunger to said stationary valve member; said annulargroove including a circumferentially extending wall section and twoaxially opposing annular wall sections, said wall sections respectivelyreceiving the regulated fluid pressure, said two opposing annular wallsections having two different pressure-receiving areas for moving saidplunger in said pressure reduction direction by reaction created by thedifference between the pressure-receiving areas; a return spring forbiasing said plunger in one axial direction; and an electromagneticsolenoid coaxially arranged on an outer periphery of said plunger, foraxially sliding said plunger against the bias of said spring in theother axial direction by an axial displacement based on a value ofexciting current applied to said solenoid.